Automatic machine for levelling heel-seats of shoes



A. MALVERDI Nov. 19, 1957 I AUTOMATIC MACHINE FOR LEVEL-LING HEEL-SEATS OF SHOES Filed July 20, 1955 4 Sheets-Sheet l S m mm mm Q Q NM NS 2 m5 S N9 vwml \N\\\\I/ m I aw efimm mm mt Vm/wm 9Q v8 m: wv mm m9 om m5 WV\ Qm m m. QQ mm 9 mm w: E m9 Q m m2 m9 N9 g vn v9 vm QM, NN W m vm u .ww Wm. H m9 mm Alessandro Ma/vera'i INVENTOR. Q0167- A. MALVERDI Nov. 19, 1957 AUTOMATIC MACHINE FOR LEVELLING HEEL-SEATS OF SHOES Filed July 20, 1955 4 Sheets-Sheet 3 Alessandra ,Malverdi INVENTOR.

A. MALVERDI Nov. 19, 1957 AUTOMATIC MACHINE FOR LEVELLING HEEL-SEATS OF SHOES Filed July 20, 1955 4 Sheets-Sheet 4 Alessandro Illa/Verdi INVENTOR.

, M MM' United States Patent Office so 2,813,283 Patented Nov.- 19, 1957 AUTUMATIC MACHINE FOR LEVELLING HEEL-SEATS OF SHOES Alessandro Malverdi, Bologna, Italy Application July 20,1955, Serial No. 523,243 Claims priority, application Italy July 22, 1954 11 Claims. (Cl. 12--53.4)

This invention comprises novel and useful improvements in an automatic machine for levelling heel-seats of shoes and more particularly pertains to an apparatus adapted for the automatic levelling or edge-finishing of the heel-seats of shoes and particularly of ladies shoes.

This application is based upon my prior Italian Patent No. 518,286 of the same title and which was filed on July 22, 1954-, and issued on March 5, 1955.

In order that the mounting of heels on shoes, and especially of ladies shoes may be performed rapidly and satisfactorily, it is essential that the part of the shoe which supports the heel, and which is known as the heel-seat, must be edge-finished in an accurate manner and adhere closely to the last of the shoe. Conventionally, this has always been effected by a manual operation, as by employing a hammer, or by the use of steel molds which are pressed onto the heel-seat and which are then hammered all around the seat until a satisfactory true shape and edge-finish has been achieved. As will be evident, the aforesaid conventional method is disadvantageous, especially for mass production of shoes, since the operator quickly tires, with a resultant drop in the quality, quantity, or both, of his Work. It is therefore the prime purpose of the present invention to provide an apparatus which will effect the automatic scat finishing or the hammering of the heel-seat in a minimum of time and with a uniform quality of the workmanship.

A further object of the invention is to provide an apparatus in accordance with the foregoing objects, wherein the hammering operation is effected by the use of compressed air and wherein a translational movement of the hammer and a rotary movement of the shoe relative to the hammer is utilized in order that the operation may be satisfactorily performed over the entire surface of the heel-seat.

A further object of the invention is to provide an apparatus wherein an automatic pneumatic hammer may be utilized to edge-finish the heel-seat of a shoe, together with improved mechanism for effecting a vertical motion of the hammer with respect to the heel-seat, accompanied by a translational movement of the hammer, and which will also coordinate a rotational movement of the shoe in conjunction with the aforesaid motions.

Important features of the invention in the apparatus disclosed in this application as an exemplification of the principles of the invention are the provision of means for pivoting the hammer for up and down movement relative to the shoe heel; the translational movement of the hammer upon its vertical pivoting means in order that the same may be moved circumferentially of the heel-seat of a shoe; mechanism for intermittently applying power from a continuous power source for causing vertical and translational movement of the hammer together with rotational movement of the shoe all in timed relation with respect to each other.

These, together with other objects and advantages which will become subsequently apparent, reside in the details of construction and operation as more fully hereinafter described and claimed, reference being had to the accompanying drawings forming a part hereof, wherein like numerals refer to like parts throughout, and in which:

Figure 1 is a view in vertical section through a satisfactory form of apparatus for carrying out the principles of this invention, the mechanism being shown in a position in which the shoe is held stationary while both a translatory and a vertical pivoting movement is imparted to the pneumatic hammer;

Figure 2 is a vertical transverse sectional view through the arrangement of Figure 1, taken at right angles to Figure 1;

Figure 3 is a diagrammatic view showing three positions of the hammer during the heel-seat finishing operation;

Figure 4 is a diagram of the electric circuit used in the apparatus;

Figure 5 is a horizontal sectional view taken substantially upon the plane indicated by the broken section lines 5-5 of Figure 1 and 55 of Figure 2;

Figure 6 is a perspective view of a friction-operated slide forming a part of the mechanism for imparting translational movement to the pneumatic hammer;

Figure 7 is a perspective view of the support structure for the hammer;

Figure 8 is a detail view in vertical section and upon an enlarged scale and showing the clutch mechanism for alternately coupling the power source to the shoe rotating means and the hammer moving means; and

Figure 9 is a detail perspective view of a portion of the manual control means for controlling the operation of the hammer translating mechanism.

The apparatus illustrated in the accompanying drawings as an exemplification only of the principles of the invention includes a housing of any suitable character and which is indicated generally by the numeral 10, the same including a bottom wall 12, a side wall or walls 14, together with a top wall 16. Upper and lower tubular guide bushings 18 and 28 are disposed in alignment and are supported by the top wall and bottom wall respectively, the upper bushing extending internally and externally of the housing as shown in Figure 1. As shown more clearly in Figure 2, the housing 10 is provided with a support arm or standard 22 which at its upper end terminates in an internally threaded member 24 which is disposed in alignment with and above the upper end of the tubular bushing 18. A clamping screw 26 is threaded through this extremity, being provided with a hand wheel 28, whereby a shoe 30 may be clamped be tween the end of the clamping screw 26 and the upper end of the tubular boss 18 as set forth hereinafter.

A shoe supporting and rotating arbor is journaled in the tubular bushing or boss 18. This arbor includes a shaft 32 having a head 34 at its upper end which rotatably rests upon the top surface of the boss 18 which constitutes a journal or bearing for the same, and which head is adapted to support the shoe 30 at the heel of the same, the shoe being clamped to this head by the clamping screw 26, as shown in Figure 1. It will thus be seen that as the arbor is rotated, the shoe will be rotated therewith to thus cause the shoe to turn about a vertical axis through the heel portion of the shoe. At its lower end, the arbor shaft 32 is provided with a plate 36 which rotatably abuts the lower end of the tubular boss 18 which latter constitutes a journal for the same, the plate 36 constituting a clutch plate as will be more apparent from Figure 8. For that purpose, the lower surface of the plate 36 is provided with a recess or socket 38 which is adapted to be intermittently and selectively engaged by a clutch member as set forth hereinafter.

Journaled in the lower tubular boss 20 upon a vertical stem or axle 40 is a clutch driving drum or member 42 having an upper surface in close sliding proximity to the clutch plate 36 carried by the arbor shaft 32. Disposed between the boss 20 and the clutch driving member 42 are a pair of pulleys, these consisting of a large pulley 43 keyed or otherwise fixedly secured to the shaft 443 for imparting rotation thereto, and a smaller pulley 44 which is freely rotatably journaled upon the shaft 41 except when clutched or locked thereto by the clutch member 42, as set forth hereinafter.

An electric motor 46, as shown in Figures 1 and 5, is secured in the casing 14 in any suitable manner as by being mounted upon the bottom wall 12, and is provided with a driving pulley 48 having a plurality of pulley grooves. Multiple driving belts 50 connect the grooves of the driving pulley 48 with corresponding multiple grooves 52 upon the previously mentioned pulley 43 whereby rotation is continuously imparted to the shaft 40 and to the clutch member 42 during the operation of the motor.

The upper surface of the pulley 44, as shown best in Figure 8, has a close fitting sliding engagement with the lower surface of the clutch member 42, and is provided with a recess or socket 54 which is adapted to be intermittently connected to the clutch member 42 in order to be driven by the same. As will be seen, the pulley 44 is provided with a'trapezoidal shaped groove 56 therein for a purpose to be subsequently set forth.

Referring especially to Figure 8, it will now be seen that the clutch member 42 has a clutch element bore 58 extending entirely therethrough and in parallel relation to the axis of the shaft 40. Slida'ble in this bore is a clutch element or pin 60 whose opposite conical extremities are adapted to be selectively and intermittently engaged in alternate driving engagement with the clutch recesses or sockets 38 and 54 of the arbor plate 36 and of the pulley 44 respectively. The clutch element or pin is hollow and is actuated by means of an actuating lever 62 journaled upon a fulcrum or pivot 64 carried by a bifurcated supporting bracket or lug 66 extending laterally from the clutch member 42. The inner end of the clutch lever terminates in a ball 68 which extends through an opening '71) in the side wall of the clutch element 60 and a pair of coil springs '72 and 74 are received in the hollow interior of the clutch element 60 and are interposed between the ball 68 and the opposite ends of the recess in the clutch element. It will thus be apparent from Figure 8 that by rotating the clutch actuating lever 62 in a clockwise direction, the clutch lever will compress the spring 72 so that when rotation of the clutch member 42 has placed the bore 58 in alignment with the socket 38, the clutch will be connected to the arbor and thereby will rotate the shoe secured to the upper end of the same. However, when the clutch lever is rotated in a counterclockWise direction, the ball 6? will compress the lower spring 74, and when the clutch element bore 58 comes into alignment with the socket 54 of the pulley 44, the clutch member 42 will be clamped to the pulley 44 for rotating the latter. It will thus be seen that the dimensions and proportions of the clutch member 42, the clutch element 611, the clutch plate 36, and the sockets 38 and 54 in the clutch pulley 36 and the pulley 44 are such that the arbor and the pulley will be operated in alternation.

Referring now especially to Figures 1 and 5, it will be seen that there are provided a pair of stationary actuating cams 8t and 32 which are carried by suitable supporting standards 84 and 36 which may be mounted upon any convenient portion of the casing 10, as upon the bottom wall thereof. These cam members are disposed at different vertical elevations and are provided with cam surfaces 88 and 90.

The cam 31) has its lower inclined cam surface 88 adapted to engage the upper side of the actuating lever, and thus will rotate the lever in a clockwise direction.

4 The cam 82 has an upper cam surface 90 which is adapted to engage the underside of the lever and will thus impart rotation to the lever in a counter-clockwise direction. These two cam members are disposed 180 apart so that upon rotation of the clutch member 42 the lever will be alternately actuated, each half revolution, upwardly or downwardly to thus intermittently and alternately impart rotation to the shoe rotating arbor or the pulley 44. As will be apparent from Figure l, the cam 80 will move the clutch lever in a direction to disconnect the pulley and to connect the shoe arbor to the clutch member, while the cam 82 will impart reverse rotation to the actuating lever and will disengage the clutch member from the arbor, thus stopping further rotation of the arbor and shoe, and coupling the clutch to the pulley 44.

Reference is next made to the pneumatic hammer, its support means, and its actuating mechanism. As shown in Figures l and 7, there is provided a pneumatic hammer indicated generally by the numeral 92 and which may be of any conventional and known design, the same includ ing a head 94 which is adapted to be vibrated against the heel-seat of the shoe 30 by means of pneumatic pressure, supplied from any suitable source as by a flexible conduit 96. Since the structure of the pneumatic hammer forms no part of the present invention, and may be of any known and conventional design, it being merely necessary that a reciprocatory movement shall be imparted to the head 94, a further description of the same is deemed to be unnecessary. The support for the hammer includes a frame consisting of a pair of support arms 98 and 104) which are fixedly connected at one end to a shaft 102. At their other ends, the arms are provided with angulated portions 104 which converge towards each other and are integrally joined to a bushing 106 which receives the pneumatic hammer 2 in any suitable manner. The shaft 1112 constitutes a horizontal axis or fulcrum pin about which the arms and the pneumatic hammer carried thereby are pivoted and also along which a translational or axial movement of the hammer and arms is eflfected. As will be seen from Figures 1 and Z, a pair of support brackets or support members 108 extend upwardly from the top wall 16 of the housing or casing 11 and the member 102 is journaled for free rotation in journal hearings in the support brackets or arms and for axial translatory movement therein. A coil compression spring 110 is disposed between one of the brackets 108 and the adjacent end of one of the arms, such as the arm 98, to yieldingly urge the member 102 to an endwise position in the supporting brackets, or towards the left as viewed in Figure 2. There is provided a lever arm 112 which at one end terminates in a tubular boss 114 which is slidably received upon the member 102. As shown clearly in Figure 7, the member 102 is provided with a longitudinally extending keyway or slot 116 and a key 118, see Figure 1, connects the lever arm 112 to the member 102 to permit relative sliding movement of the support arm assembly of a pneumatic hammer but prevents relative rotation therebetween. As will be seen from Figure 2, the boss 114 is retained between the brackets 108 in a manner to permit rotation but to prevent lateral translatory or axial movement of the boss and of the arm. Consequently, vertical oscillation of the lever arm 112 will cause a pivoting movement of the support arm assembly and of the pneumatic hammer, while at the same time an axial or translatory movement of the member 102 and of the hammer and support arms carried thereby can be effected without corresponding movement of the lever arm 112. At its lower end, the lever arm 112 has a bifurcated portion 119 which is received within the bifurcated extremity 121 of a pitman 120, being connected thereto as by a pin 122, see Figure 5, which extends through these two bifurcated portions. As shown most clearly in Figures l and 5, the pitman is journaled upon a crank pin 124 carried by the upper surface of the pulley 48 so that as the pulley 48 is, rotated by the motor 46, the

.and thus yieldingly urges the roller crank pin 124 and the pitman 120 will be continuously operated, and in turn will impart continuous vertical oscillation to the lever arm 112 and thus to the support arm assembly and the pneumatic hammer. This vertical oscillation will cause the hammer to move up and down relative to the heel-seat of the shoe during its hammering operation, and upon whatever portion of the shoe is presented thereto during intermittent rotation of the shoe by the previously described arbor mechanism.

Attention is next directed to the mechanism for imparting a translational movement to the support arm assembly and the pneumatic hammer along the axis of the shaft or element 192. Referring now to Figures 1, 2 and 5, it will be seen that a flexible member 130 in the form of a cable or strap has one end secured to the support arm assembly, as to the end of the arm 98, see Figure 2,

by means of any suitable attachment as at 132. This cable is entrained over a guide pulley 134 journaled on an axle 1336 which is carried by the top wall 16 of the casing, as shown in Figure 1, The cable extends through an opening 138 in the top wall of the casing and from thence is entrained over a second guide pulley 140, journaled upon an axle 142 carried by the side wall 14, as will be apparent from Figures 1 and 5. The other extremity of the cable, as shown in Figures 1 and 5, is connected as at 144 to the bifurcated end portion 146 of a slide bar 143. The construction of this slide bar as shown best in Figure 6 includes a trapezoidal shaped rib 150 which is complementary to the previously mentioned trapezoidal groove 56 of the pulley 44 and is adapted to frictionally engage the same as set forth hereinafter. At its other extremity, the slide bar has a projecting stem portion 152 terminating in a diametrically reduced portion 154 with an annularly enlarged flange 156 between the portions 152 and 154.

As shown more clearly in Figure, 1, a compression spring 158 has one end embracing the portion 152 which constitutes a seat and guide therefor, with the flange 156 constituting an abutment for the end of the spring, whose other extremity is received within a socket 160 formed in a tubular extension 162projecting laterally from the side wall 14. It will thus be seen that the compression spring yieldingly urges the slide in a direction to release tension upon the cable 130, and when such tension is released, the previously mentioned coil spring 110 will move the hammer support arm assembly toward one position of its translatory travel. Means are provided for frictionally engaging or pressing the longitudinal trapezoidal rib 150 into engagement with the correspondingly shaped groove 56 of the pulley 44. This control means, as shown best in Figures 2, 5 and the detail of Figure 9, consists of an antifriction roller 166 which is journaled upon a pin 168 mounted in a vertical bore in the extremity 1711 of a control lever 172. The wall 14 of the casing is provided with inwardly extending apertured brackets or ears 174 between which an intermediate portion of the lever 172 is journaled as by a vertically disposed pivot pin or axle 176. The lever extends through a slot 178 in the side wall and is provided with a fingergrip portion 180 whereby horizontal swinging movement may be imparted to the lever with a corresponding horizontal swinging movement of the anti-friction roller 166. At its upper end, the pin 168 is provided with a diametrically reduced upwardly projecting extension 182 which is received in a bore 184 in the stem 186 of a plunger or piston 188 which is slidably received within an inwardly projecting sleeve 191) carriecl by the side wall. A coil spring 192 therein urges the plunger outwardly thereof 166 in one direction of its horizontal travel. There is a looseness of fit between the pin 182 and the bore 184 of the piston rod 176; and between the piston 188 and its cylinder 190 whereby to allowthe necessary rocking motion of the lever 172 and roller 166., The longitudinal axis of the piston rod 186 may also be sufliciently inclined to that of the lever arm carrying the roller 166 to permit the spring 192 to bias the roller towards the slide 148 and the latter towards the pulley 44. The arrangement is such that the spring H2 will normally move the roller in a direction to engage the same with the slide until released by manual operation of the lever 172-. The spring 158 tends to move the slide towards the right as viewed in Figure 5. However, when the control lever 172 is actuated by spring 192 to cause the pressure roller 166 thereof to press against the slide 148, the longitudinal rib 150 thereof is pressed into good frictional engagement with the groove 56 of the pulley 44 so that rotation of the pulley will move the slide towards the left, against the resistance of the return spring 153, as viewed in Figures 1 and 5, and thus tension the cable and thereby move the support arm assembly towards the right, as viewed in Figure 2. This will result in causing a lateral or translatory motion to the pneumatic hammer, and thus cause the same to move horizontally along the heel-seat.

The translatory movement of the hammer may be accompanied by rotation of the shoe upon its arbor by the rotating mechanism previously described, so that as indicated in Figure 3 the hammer may be moved from the position shown at A, B, and C, the shoe being rotated 180 from position D to position E, to thus permit the hammer to work upon both sides of the heel-seat of the shoe.

It will be noted that the slide 148 is held in position by the engagement of the rib in the groove 56 of the pulley 44- and by the position of the roller 166; as well as by the operation of the spring 158 and the cable tensioning member 130. If desired, however, structural guide members may also be applied to limit the slide to rectilinear reciprocation.

From the above description, it will beunderstood that in the 360 rotation of the clutch member 42, the pneumatic hammer is oscillated vertically about its pivotal support upon the member 102 by the mechanism driving the lever arm 112, causing the hammer to be displaced vertically and travel vertically along the surface of the heel-seat during the vibrations of the hammer. It will also be noted that during of this rotation, the shoe is stationary by virtue of the engagement of the clutch element with the pulley 44 and its disengagement from the arbor, and a translatory motion is imparted to the hammer through the slide mechanism previously mentioned.

As will be apparent, the slide 148, after being frictionally driven to one end of its travel, would not be able to return to its original position to repeat the operation except for the provision of the manual control lever 172 which, being within reach of the operator, is manually manipulated to release the pressure of the roller 166 and thereby permit the spring 158 to return the slide to its original position and further permit the spring 110 to return to the hammer support arms to their original position in readiness for the next transverse movement of the same.

Referring now to the diagrammatic view of Figure 4, which discloses a suitable electric circuit for operating the motor, which it is assumed is to be started by the operator and stopped automatically, the feed line to the motor is controlled by a relay switch which is electromagnetically operated in response to the manual closing of the switch 192 by the operator. The switch 190 thus closes the circuit and starts the operation of the motor 46 and remains operative owing to an auxiliary contact 194 arranged on the movable member of the solenoid switch 190 whereby the supply of current to the motor cannot be cut off by any external means without the circuit of the switch 190 being broken. This circuit will be broken at the closed contact 196 by the pressure of the slide 148 when the latter reaches the end of its working stroke, an arm 198 being carried by the slide and positioned to 7 operate the switch 196. When the circuit is broken by the switch 196, the electro-magnetic relay switch 190 is de-energized and the switch 194 is then opened. The motor can then only be started by the action of the operator on the push button switch 192.

The operation of the pneumatic hammer upon the heelseat of the shoe is as follows. In the starting position of the device, the pneumatic hammer is in the position indicated at A in Figure 3. Compressed air is supplied to the hammer and electric current to the motor and the hammer starts to beat the heel-seat of the shoe 3t), oscillating up and down upon the heel-seat as it travels cir-- cumferentially about the seat and at the same time as it is displaced uniformly towards the position B while the shoe remains stationary. During this operation, the clutch member 42 is clutched to the pulley 44, and the operation of the slide by the frictional drive has caused the above mentioned translatory movement of the hammer. When the position B is reached, the pneumatic hammer ceases to be displaced or shifted laterally and continues to. beat the heel-seat and to oscillate while the shoe now starts to rotary movement since the clutch control lever is shifted to engage the clutch with the arbor shaft 32 and to disengage the clutch from the pulley 44. As will be seen from Figure 8, the clutch pin 60 cannot disengage from either the socket 54 or 38 until these sockets are aligned, and hence there will be no opportunity for relative slippage between the members at the time the clutch pin: is released from one .member and engaged with the other. Frictional resistance between the members 42, 44. and 43, or any other desired means may be employed to prevent return of the slide 148 until the pressure of the latter upon the pulley 44 is released by manual actuation of the lever 172. Rotation of the shoe is stopped after it has travelled through 180 by the alternate operation of the cams 80 and 82 upon the clutch actuating lever 62. The pneumatic hammer again beginsto advance until it reaches the position C. Figure 3 thus shows the distribution of the movements which take place throughout the entire cycle of operation of the system involving the members 42, 44, and 36.

The starting position of the pneumatic hammer is on the axis; of the position A with the shoe stationary; then the members. 42. and 44 are rotated through 90 and the hammer arrives at the position B. Subsequent rotation of the members 42 and 36 takes place through 180, the hammer remaining stationary, although continuing its vibratory operation, and the shoe is rotated. Subsequent rotation of the members 42 and 44' takes place through 909, the hammer being displaced from the position B to the position G with the shoe stationary. It will thus be apparent from the above that for each cycle of operation the clutch member 42 moves through 360, the pulley 44 through 180 in two stages, and the arbor clutch member 36 turns through 180 in a single period.

In clamping the shoe upon the arbor assembly, it is preferred to place the shoe over the arbor head 34, and then center a steel mold on the heel-seat, with the screw clamp 26 pressing against this mold. Thus, the shoe is firmly fixed and secured to the arbor for rotation therewith during the operation of this apparatus. When the machine stops automatically, by actuation of the cut-off switch 196 by the arm 198 at the end of the stroke of the slide 148, the operator removes the shoe and actuates the control lever 172, which releases the frictional engagement between the slide 148 and the pulley 44 and permits the spring 158 to return the slide to its original position and permits the shifting mechanism for imparting translatory motion to the support arm assembly of the hammer to also return it to its original position in readiness for the operation upon the next shoe.

The foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly all suitable modifications and equivalents may be resorted to, falling within the scope of the invention as claimed.

What is claimed as new is as follows:

1. A shoe heel finishing machine comprising a sup port for a shoe, a hammer for beating the heel-seat of a shoe mounted upon said shoe support for edge-finishing the shoe heel-seat, means for imparting vibrations to the hammer, and means for moving the hammer relative to the shoe heel during vibration of the hammer, said last means including means for causing oscillatory movement of the hammer in a vertical plane, means for rotating the heel-seat about a vertical axis, and means for causing rectilinear translatory movement of the hammer in a horizontal plane.

2. A shoe heel finishing machine comprising a support for a shoe, a. hammer for beating the heel-seat of a shoe mounted upon said shoe support for edge-finishing the shoe heel-seat, means for imparting vibrations to the hammer, and means for moving the hammer relative to the shoe heel during vibration of the hammer, means for rotating the heel-seat about a vertical axis during vibration of said hammer, and means for causing rectilinear translatory movement of the hammer in a horizontal plane.

3. A shoe heel finishing machine comprising an arbor for supporting a shoe for horizontal rotation about a vertical axis through the heel of the shoe, a hammer, means for causing vibration of said hammer, means supporting said hammer, operating means for vertically oscillating said hammer, operating means for rectilinearly reciprocating. said hammer in a horizontal plane, and rotating means for rotating said arbor.

4. The combination of claim 3 including a driving means including a rotating member, and a clutch connecting said driving means alternately to each said operating means during rotation of the rotating memher.

5. The combination of claim 3 including a driving means including a rotating member, and a clutch connecting said driving means alternately to each said operating means during 180 rotation of the rotating member, said rotating member having a clutch actuating lever mounted. thereon and rotating therewith, stationary means for operating said lever in opposite directions.

6. The combination of claim 3 wherein said hammer supporting means includes a horizontal shaft, arms on said shaft carrying said hammer, and journals in which saidshaft is mounted for axial and rotary movement.

7. The combination of claim 3 wherein said hammer supporting means includes a horizontal shaft, arms on said shaft carrying said hammer, journals in which said shaft ismounted for axial and rotary movement, said operating means for vertically oscillating the hammer including a lever armkeyed to said shaft, and means for continuously oscillating said lever arm.

8. The combination of claim 3 wherein said hammer supporting means includes a horizontal shaft, arms on said shaft carrying said hammer, and journals in which said shaft is mounted for axial and rotary movement, said operating means for rectilinearly reciprocating said hammer including a spring operatively associated with said shaft for yieldingly moving the shaft and arms to a first position and actuating means for axially shifting the shaft and arms to a different position.

9. The combination of claim 3 wherein said hammer supporting means includes a horizontal shaft, arms on said shaft carrying said hammer, and journals in which said shaft is mounted for axial and rotary movement, said; operating means for rectilinearly reciprocating said hammer including a spring operatively associated with said shaft for yieldingly moving the shaft and arms to a first position and actuating means for axially shifting the shaft and arms to a different position, said actuating means including a slide, a cable connecting said slide to said shaft, and driving means for imparting movement to said slide.

19. The combination of claim 3 wherein said hammer supporting means includes a horizontal shaft, arms on said shaft carrying said hammer, and journals in which said shaft is mounted for axial and rotary movement, said operating means for rectilinerly reciprocating said hammer including a spring operatively associated with said shaft for yieldingly moving the shaft and arms to a first position and actuating means for axially shifting the shaft and arms to a different position, said actuating means including a slide, a cable connecting said slide to said shaft, and driving means for imparting movement to said slide, said driving means including a pulley, said slide having a rib frictionally engageable with said pulley, and pressure means yieldingly urging the slide into frictional engagement with the pulley.

11. The combination of claim 3 wherein said hammer supporting means includes a horizontal shaft, arms on said shaft carrying said hammer, and journals in which said shaft is mounted for axial and rotary movement,

said operating means for rectilinearly reciprocating said hammer including a spring operatively associated with said shaft for yieldingly moving the shaft and arms to a first position and actuating means for axially shifting the shaft and arms to a dilferent position, said actuating means including a slide, a cable connecting said slide to said shaft, and driving means for imparting movement to said slide, said driving means including a pulley, said slide having a rib frictionally engageable with said pulley, pressure means yieldingly urging the slide into frictional engagement with the pulley, and release means manually operable for disengaging the pressure means from the slide to release the frictional engagement of the slide and pulley.

References Cited in the file of this patent UNITED STATES PATENTS 1,013,971 Tierney Jan. 9, 1912 1,143,717 La Chapelle June 22, 1915 FOREIGN PATENTS 383,855 Great Britain Nov. 24, 1932 575,651 Germany May 3, 1933 600,818 Germany Aug. 1, 1934 

